US3947153A - Lubricated thrust bearings for pump and motor units - Google Patents

Lubricated thrust bearings for pump and motor units Download PDF

Info

Publication number
US3947153A
US3947153A US05/489,421 US48942174A US3947153A US 3947153 A US3947153 A US 3947153A US 48942174 A US48942174 A US 48942174A US 3947153 A US3947153 A US 3947153A
Authority
US
United States
Prior art keywords
bearing
housing
shaft
disk
combination
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/489,421
Other languages
English (en)
Inventor
Heinz-Bernd Matthias
Christian Klepp
Gunter Koll
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Klein Schanzlin and Becker AG
Original Assignee
Klein Schanzlin and Becker AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Klein Schanzlin and Becker AG filed Critical Klein Schanzlin and Becker AG
Application granted granted Critical
Publication of US3947153A publication Critical patent/US3947153A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/048—Bearings magnetic; electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/06—Sliding-contact bearings for exclusively rotary movement for axial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0402—Bearings not otherwise provided for using magnetic or electric supporting means combined with other supporting means, e.g. hybrid bearings with both magnetic and fluid supporting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0442—Active magnetic bearings with devices affected by abnormal, undesired or non-standard conditions such as shock-load, power outage, start-up or touchdown
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/0476—Active magnetic bearings for rotary movement with active support of one degree of freedom, e.g. axial magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/002—Cooling of bearings of fluid bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/005—Cooling of bearings of magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/09—Structural association with bearings with magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps

Definitions

  • the present invention relates to improvements in pump and motor units, especially in hermetically sealed pump and motor units wherein an electric motor (preferably a wet motor) drives a centrifugal pump for circulation of water or another hydraulic fluid in a boiler or the like. More particularly, the invention relates to improvements in thrust bearing assembles for axially movable, axially stressed motor shafts in pump and motor units.
  • Boiler circulators in the form of pump and motor units must frequently operate at extremely high system pressures and temperatures. Such units must remain effective during each and every stage of operation including one or more stages during which the temperature and/or pressure of circulated fluid fluctuates within an extremely wide range.
  • Many recent types of boilers employ at least one but normally two pairs of pump and motor units which are connected in parallel. When the boiler is started, one of the units normally operates under overload prior to starting of the other unit or units. At such stage of boiler operation, the operating point of the one unit is well within the overload range so that axial stresses upon the motor shaft which carries the impeller of the pump are extremely high due to suction which develops in the region of the impeller and causes a pronounced rise in axial and radial stresses.
  • An object of the invention is to provide a novel and improved thrust bearing assembly for use in pump and motor units, especially in pump and motor units which are utilized to circulate water in boilers and wherein a wet motor drives a glandless centrifugal pump whose impeller is attached to the motor shaft.
  • Another object of the invention is to provide a thrust bearing assembly which can be used as a superior substitute for thrust bearings in presently known pump and motor units and whose mounting necessitates minor changes in the design of existing units.
  • a further object of the invention is to provide a bearing assembly which embodies at least one safety feature so that it can continue to take up axial stresses even if its main bearing breaks down or is rendered ineffective due to an accident or on purpose.
  • An additional object of the invention is to provide a thrust bearing assembly which can take up extremely high axial stresses including those occuring as a result of cavitation and stresses which develop due to rotation of the motor shaft at a very low speed, which operates satisfactorily even if the coolant which surrounds the bearing assembly contains solid particles, which occupies little room, and which is constructed and assembled in such a way that at least one group of its components is always held in a position of readiness to take up all or some axial stresses if another group of components breaks down or is rendered ineffective, either accidentally or on purpose.
  • the invention is embodied in a pump and motor unit, especially in a pump and motor unit wherein a wet electric motor drives a centrifugal pump for circulation of water or another hydraulic fluid whose pressure and/or temperature fluctuates within an extremely wide range.
  • the improved unit comprises a liquid-containing housing, a shaft which is rotatably mounted in the housing and has at least some freedom of axial movement therein, a preferably double-acting main thrust bearing which is in contact with liquid in the housing and includes a disk on the shaft and electromagnet means provided in the housing adjacent to the disk and being energizable to produce an electromagnetic field which normally maintains the disk and the shaft in a predetermined axial position with respect to the housing, and at least one preferably double-acting mechanical auxiliary thrust bearing for the shaft.
  • the parts of the auxiliary bearing are in contact with liquid in the housing.
  • the electromagnet means defines with the disk at least one clearance and the pump and motor unit may further comprise means for regulating the strength of the electromagnetic field as a function of changes in the width of the clearance in response to variations of axial stresses upon the shaft.
  • the one auxiliary bearing may comprise a radially extending surface on the disk and a surface on the electromagnet means. The two surfaces are out of contact with each other in energized condition of the electromagnet means and engage with each other in response to axial stressing of the shaft in deenergized condition of the electromagnet means.
  • the auxiliary bearing includes a radially extending first surface on the disk adjacent to the electromagnet means and a second surface provided on the housing adjacent to the first surface and surrounding the electromagnet means (i.e., the distance between the axis of the shaft and the electromagnet means is less than the distance between the axis of the shaft and the second surface).
  • the two surfaces are disengaged from each other in energized condition of the electromagnet means and engage with each other in response to axial stressing of the shaft in deenergized condition of the electromagnet means.
  • the arrangement is preferably such that the distance between the two surfaces is energized condition of the electromagnet means is less than the distance between the first surface and the electromagnet means so that the first surface remains out of contact with the electromagnet means when the latter is deenergized so that the first surface engages the second surface in response to axial stressing of the shaft.
  • the disk may comprise means for circulating the liquid in the housing; such circulating means may comprise one or more substantially radially extending channels or passages each having an intake end nearer to and a discharge end remote from the axis of the shaft.
  • the auxiliary bearing may constitute a Kingsbury thrust bearing which is spaced apart from the main thrust bearing, as considered in the axial direction of the shaft.
  • FIG. 1 is a fragmentary axial sectional view of an electric motor which drives a centrifugal pump and whose shaft is mounted in a bearing assembly embodying one form of the invention
  • FIG. 2 is a fragmentary axial sectional view of a motor embodying a modified bearing assembly.
  • FIG. 1 shows the housing H of an electric motor (e.g., a 3-phase squirrel cage induction type wet motor) which drives the impeller of a centrifugal pump (not shown).
  • the pump and motor unit is used for circulation of a hydraulic fluid in a boiler, and the pump is preferably of the glandless type.
  • the housing H contains electromagnets 1 which cooperate with a disk 3 on the motor shaft 2 to form therewith a main or primary axial or thrust bearing.
  • the electromagnets 1 act on both sides of the disk 3 and their electromagnetic field takes up the axial stresses which are transmitted to the disk 3 and motor shaft 2 by the impeller of the pump in the boiler.
  • the shaft 2 further rotates in a mechanical thrust bearing 4 which constitutes an auxiliary or emergency axial bearing and becomes effective when the supply of electrical energy to the electromagnets 1 is interrupted. This insures that the unit remains operative even if the primary thrust bearing is out of commission, e.g., until the cause of the interruption of energy supply is detected and eliminated or while the boiler is in the process of being shut down.
  • auxiliary thrust bearing 4 It is also within the purview of the invention to omit the auxiliary thrust bearing 4 and to use the assembly of parts 1, 3 as a combined primary and auxiliary thrust bearing. Such function is performed by the neighboring surfaces 5 of the disk 3 and electromagnets 1.
  • That portion of the housing H which contains the thrust bearings is completely filled with a cooling liquid which also serves to cool the thrust bearings, especially the primary bearing 1, 3.
  • the disk 3 is formed with at least one but preferably two or more substantially radially extending passages or channels 6 which draw the liquid at their inner ends and discharge the liquid at their outer ends to thus insure an effective cooling of the disk by streams of continuously circulating liquid.
  • the liquid withdraws heat from the primary bearing as well as from the auxiliary bearing 4.
  • such circulation insures a more satisfactory lubrication of moving parts including the shaft 2 and the components of the two thrust bearings as well as the evacuation of contaminants (especially solid particles of dirt) from the clearances 7 and/or the clearances between the parts of the auxiliary thrust bearing 4.
  • the flow of liquid in the housing H is indicated by arrows.
  • the auxiliary bearing 4 is a double-acting Kingsbury type bearing and comprises a chromium-plated chrome-steel disk 2a which is affixed to the shaft 2, ring-shaped pads 4a at both sides of the disk 2a, and ring-shaped shoes 4b in the housing H.
  • the pads 4a are disposed between the shoes 4b and the respective sides of the disk 2a.
  • the clearances 7 between the electromagnets 1 and the surfaces of the disk 3 are relatively wide so as to insure that the main thrust bearing can take up extremely high stresses without permitting the disk 3 to contact the electromagnets, as long as the latter remain connected to the source of electrical energy. This guarantees that the neighboring surfaces 5 of the parts 1, 3 are normally out of contact with each other and the primary thrust bearing is not subjected to any wear as a result of friction.
  • the unit preferably further comprises means for monitoring the width of clearances between the disk 3 and electromagnets 1, and for regulating the intensity of electromagnetic fields when the width of such clearances is outside of a preselected range.
  • the width of clearances can be monitored directly (i.e., by continuously measuring the distance between the one or the other side of the disk 3 and the adjacent electromagnet 1) or indirectly by monitoring the axial position of the motor shaft 2 which is rigid with the disk 3.
  • the monitoring means preferably comprises a proximity probe whose output supplies electric signals having an intensity which is proportional to the width of the clearance between one side of the disk 3 and the respective electromagnet 1.
  • the disk 3 can be permitted to directly engage the adjacent surfaces of the electromagnets 1.
  • the unit can be modified in a manner as shown in FIG. 2.
  • the housing HH includes two annular sections 8, 9 into which the electromagnets 1 are embedded so that the surfaces 8a, 9a of the sections 8, 9 are nearer to the disk 3 than the surfaces 1a of the electromagnets.
  • the disk 3 engages the surface 8a or 9a but remains spaced apart from the surfaces 1a to thus avoid the wear upon the electromagnets.
  • the surfaces 8a, 9a surrounds the electromagnets 1, i.e., that the loci of mechanical contact between the disk 3 and housing section 8 or 9 are more distant from the axis of shaft 2 than the electromagnets 1.
  • the sections 8, 9 with annular surfaces (indicated at 8b, 9b) which are nearer to the axis of the shaft 2 than the electromagnets 1 or to provide the section 8 and/or 9 with two surfaces (8a, 8b and/or 9a, 9b) which can engage the disk 3 when the primary thrust bearing is out of commission.
  • the flow of liquid in the housing HH is indicated by arrows.
  • the improved thrust bearing arrangement can be used with equal advantage in all such establishments wherein the impeller of a pump is subjected to substantial axial stresses which are normally taken up by a primary thrust bearing and wherein at least one auxiliary thrust bearing is needed or desirable to take up axial stresses when the primary bearing is disconnected or out of commission.
  • the bearing arrangement can be used to circulate a liquid in a boiling water reactor.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Power Engineering (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
US05/489,421 1973-07-18 1974-07-17 Lubricated thrust bearings for pump and motor units Expired - Lifetime US3947153A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DT2336488 1973-07-18
DE19732336488 DE2336488A1 (de) 1973-07-18 1973-07-18 Axiallagerung fuer kreiselpumpen

Publications (1)

Publication Number Publication Date
US3947153A true US3947153A (en) 1976-03-30

Family

ID=5887272

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/489,421 Expired - Lifetime US3947153A (en) 1973-07-18 1974-07-17 Lubricated thrust bearings for pump and motor units

Country Status (6)

Country Link
US (1) US3947153A (enrdf_load_stackoverflow)
CS (1) CS175480B2 (enrdf_load_stackoverflow)
DE (1) DE2336488A1 (enrdf_load_stackoverflow)
GB (1) GB1454205A (enrdf_load_stackoverflow)
IT (1) IT1015527B (enrdf_load_stackoverflow)
PL (1) PL91412B1 (enrdf_load_stackoverflow)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4025240A (en) * 1974-07-10 1977-05-24 Sperry Rand Corporation Geothermal energy control system and method
US4033877A (en) * 1974-07-22 1977-07-05 Klein, Schanzlin & Becker Aktiengesellschaft Cyclone for removing solid impurities from liquid in a pump and motor unit
US4042847A (en) * 1974-07-10 1977-08-16 Grundfos A/S Liquid-filled submersible electromotor
US4065234A (en) * 1975-12-22 1977-12-27 Nihon Kagaku Kizai Kabushiki Kaisha Magnetically driven rotary pumps
US4082376A (en) * 1974-12-06 1978-04-04 Arthur Pfeiffer Vakuumtechnik Wetzlar Gmbh Bearing arrangement
US4131396A (en) * 1977-04-07 1978-12-26 Sundstrand Corporation Hermetic compressor lubrication system with two-stage oil pump
US4413863A (en) * 1980-08-07 1983-11-08 Centre D'etudes Et De Recherches De La Machine-Outil (C.E.R.M.O.) Hydrostatic support device
US4502851A (en) * 1982-11-12 1985-03-05 Vaughn Calvin Pivotal discharge apparatus
US4768888A (en) * 1987-04-29 1988-09-06 Mcneil (Ohio) Corporation Unitary bearing member and motor incorporating the same
US4886430A (en) * 1988-07-18 1989-12-12 Westinghouse Electric Corp. Canned pump having a high inertia flywheel
US4929158A (en) * 1987-04-09 1990-05-29 Societe Europeenne De Propulsion Turbopump with actine suspension for a propulsion system
US5765950A (en) * 1996-11-29 1998-06-16 Goulds Pumps, Incorporated Thrust bearing assembly
US6057619A (en) * 1998-12-22 2000-05-02 Sundstrand Corporation Stress relief in a magnetic thrust bearing
US20070025865A1 (en) * 2005-07-29 2007-02-01 Ksb Aktiengesellschaft Electric motor having a coaxially associated pump
US20070090705A1 (en) * 1999-09-30 2007-04-26 Mitsubishi Denki Kabushiki Kaisha Axial magnetic bearing apparatus
US20110052109A1 (en) * 2009-08-28 2011-03-03 Dresser-Rand Company Hydrostatic auxiliary bearing for a turbomachine
US20110085753A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system with oil ring for magnetically supported rotor system
US20110085752A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system for magnetically supported rotor system
US20110084563A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system with plurality of inertia rings for magnetically supported rotor system
US20110085754A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system with oil reservoir for magnetically supported rotor system
US20120160327A1 (en) * 2010-12-17 2012-06-28 Vetco Gray Scandinavia As System and method for momentary hydrostatic operation of hydrodynamic thrust bearings in a vertical fluid displacement module
RU2458446C1 (ru) * 2011-01-24 2012-08-10 Владимир Петрович Глазков Электрическая машина
US8353633B2 (en) 2010-01-15 2013-01-15 Dresser-Rand Company Bearing assembly support and adjustment system
CN108779800A (zh) * 2016-03-18 2018-11-09 诺沃皮尼奥内技术股份有限公司 用于涡轮机械的磁性轴承
US20190154048A1 (en) * 2016-03-16 2019-05-23 Schaeffler Technologies AG & Co. KG Vehicle having a pump device

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3343186A1 (de) * 1983-11-29 1985-06-05 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V., 8000 München Magnetische rotorlagerung
DE3580275D1 (de) * 1985-07-09 1990-11-29 Howden James & Co Ltd Gasumwaelzanlage.
US4623269A (en) * 1985-07-22 1986-11-18 Westinghouse Electric Corp. Wheel bearing protection apparatus
DE3715216A1 (de) * 1987-05-07 1988-11-17 Doll Robert Tauchpumpe, insbesondere fuer tiefsiedende fluessigkeiten
FR2615054A1 (fr) * 1987-05-07 1988-11-10 Makkouk Souheil Procede et dispositif pour economiser l'energie consommee par mouvements rotatifs
DE3740295A1 (de) * 1987-11-27 1989-06-08 Asea Brown Boveri Axiales magnetlager
FR2630792B1 (fr) * 1988-04-29 1992-03-06 Mecanique Magnetique Sa Palier auxiliaire a stator en graphite pour arbre tournant monte sur paliers magnetiques
RU2406878C1 (ru) * 2009-07-27 2010-12-20 Открытое акционерное общество "Центральное конструкторское бюро машиностроения" Электромагнитное разгрузочное устройство главного циркуляционного насосного агрегата
DE102011083809A1 (de) 2010-09-30 2012-04-05 Ksb Aktiengesellschaft Wellenlagerung bei Kreiselpumpen
RU2657406C1 (ru) * 2017-01-10 2018-06-13 Акционерное Общество "Центральное Конструкторское Бюро Машиностроения" Электромагнитное разгрузочное устройство главного циркуляционного насосного агрегата

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2526443A (en) * 1945-11-23 1950-10-17 Gen Electric Electric motor-driven pump
US2583583A (en) * 1948-10-20 1952-01-29 John R Mangan Compressor pump
US2809590A (en) * 1954-01-29 1957-10-15 Robert J Brown Electric motor driven pump
US2942555A (en) * 1957-04-15 1960-06-28 Rinaldo F Pezzillo Combination pump and motor
US3201182A (en) * 1962-03-28 1965-08-17 Gen Motors Corp Thrust bearing
US3565495A (en) * 1969-08-05 1971-02-23 Cambridge Thermionic Corp Magnetic suspension apparatus
US3731984A (en) * 1970-10-22 1973-05-08 H Habermann Magnetic bearing block device for supporting a vertical shaft adapted for rotating at high speed
US3791704A (en) * 1971-08-06 1974-02-12 Cambridge Thermionic Corp Trimming apparatus for magnetic suspension systems
US3811740A (en) * 1971-04-24 1974-05-21 Cnen Self-centering rotary magnetic suspension device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2526443A (en) * 1945-11-23 1950-10-17 Gen Electric Electric motor-driven pump
US2583583A (en) * 1948-10-20 1952-01-29 John R Mangan Compressor pump
US2809590A (en) * 1954-01-29 1957-10-15 Robert J Brown Electric motor driven pump
US2942555A (en) * 1957-04-15 1960-06-28 Rinaldo F Pezzillo Combination pump and motor
US3201182A (en) * 1962-03-28 1965-08-17 Gen Motors Corp Thrust bearing
US3565495A (en) * 1969-08-05 1971-02-23 Cambridge Thermionic Corp Magnetic suspension apparatus
US3731984A (en) * 1970-10-22 1973-05-08 H Habermann Magnetic bearing block device for supporting a vertical shaft adapted for rotating at high speed
US3811740A (en) * 1971-04-24 1974-05-21 Cnen Self-centering rotary magnetic suspension device
US3791704A (en) * 1971-08-06 1974-02-12 Cambridge Thermionic Corp Trimming apparatus for magnetic suspension systems

Cited By (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4025240A (en) * 1974-07-10 1977-05-24 Sperry Rand Corporation Geothermal energy control system and method
US4042847A (en) * 1974-07-10 1977-08-16 Grundfos A/S Liquid-filled submersible electromotor
US4033877A (en) * 1974-07-22 1977-07-05 Klein, Schanzlin & Becker Aktiengesellschaft Cyclone for removing solid impurities from liquid in a pump and motor unit
US4082376A (en) * 1974-12-06 1978-04-04 Arthur Pfeiffer Vakuumtechnik Wetzlar Gmbh Bearing arrangement
US4065234A (en) * 1975-12-22 1977-12-27 Nihon Kagaku Kizai Kabushiki Kaisha Magnetically driven rotary pumps
US4131396A (en) * 1977-04-07 1978-12-26 Sundstrand Corporation Hermetic compressor lubrication system with two-stage oil pump
US4413863A (en) * 1980-08-07 1983-11-08 Centre D'etudes Et De Recherches De La Machine-Outil (C.E.R.M.O.) Hydrostatic support device
US4502851A (en) * 1982-11-12 1985-03-05 Vaughn Calvin Pivotal discharge apparatus
US4929158A (en) * 1987-04-09 1990-05-29 Societe Europeenne De Propulsion Turbopump with actine suspension for a propulsion system
US4768888A (en) * 1987-04-29 1988-09-06 Mcneil (Ohio) Corporation Unitary bearing member and motor incorporating the same
US4886430A (en) * 1988-07-18 1989-12-12 Westinghouse Electric Corp. Canned pump having a high inertia flywheel
US5765950A (en) * 1996-11-29 1998-06-16 Goulds Pumps, Incorporated Thrust bearing assembly
US6057619A (en) * 1998-12-22 2000-05-02 Sundstrand Corporation Stress relief in a magnetic thrust bearing
US7274123B2 (en) * 1999-09-30 2007-09-25 Mitsubishi Denki Kabushiki Kaisha Axial magnetic bearing apparatus
US20070096573A1 (en) * 1999-09-30 2007-05-03 Mitsubishi Denki Kabushiki Kaisha Axial magnetic bearing apparatus
US20070103021A1 (en) * 1999-09-30 2007-05-10 Mitsubishi Denki Kabushiki Kaisha Axial magnetic bearing apparatus
US7235907B2 (en) * 1999-09-30 2007-06-26 Mitsubishi Denki Kabushiki Kaisha Axial magnetic bearing apparatus
US7285887B2 (en) * 1999-09-30 2007-10-23 Mitsubishi Denki Kabushiki Kaisha Axial magnetic bearing apparatus
US20070090705A1 (en) * 1999-09-30 2007-04-26 Mitsubishi Denki Kabushiki Kaisha Axial magnetic bearing apparatus
US8079833B2 (en) 2005-07-29 2011-12-20 Ksb Aktiengesellschaft Electric motor having a coaxially associated pump
US20070025865A1 (en) * 2005-07-29 2007-02-01 Ksb Aktiengesellschaft Electric motor having a coaxially associated pump
US20110052109A1 (en) * 2009-08-28 2011-03-03 Dresser-Rand Company Hydrostatic auxiliary bearing for a turbomachine
US8465207B2 (en) 2009-10-09 2013-06-18 Dresser-Rand Company Auxiliary bearing system with oil reservoir for magnetically supported rotor system
US20110085754A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system with oil reservoir for magnetically supported rotor system
US20110085752A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system for magnetically supported rotor system
US20110084563A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system with plurality of inertia rings for magnetically supported rotor system
US8283825B2 (en) 2009-10-09 2012-10-09 Dresser-Rand Company Auxiliary bearing system with plurality of inertia rings for magnetically supported rotor system
US8308364B2 (en) 2009-10-09 2012-11-13 Dresser-Rand Company Auxiliary bearing system for magnetically supported rotor system
US8408806B2 (en) 2009-10-09 2013-04-02 Dresser-Rand Company Auxiliary bearing system with oil ring for magnetically supported rotor system
US20110085753A1 (en) * 2009-10-09 2011-04-14 Dresser-Rand Company Auxiliary bearing system with oil ring for magnetically supported rotor system
US8353633B2 (en) 2010-01-15 2013-01-15 Dresser-Rand Company Bearing assembly support and adjustment system
US9568013B2 (en) 2010-12-17 2017-02-14 Vetco Gray Scandinavia As Method for momentary hydrostatic operation of hydrodynamic thrust bearings in a vertical fluid displacement module
US20120160327A1 (en) * 2010-12-17 2012-06-28 Vetco Gray Scandinavia As System and method for momentary hydrostatic operation of hydrodynamic thrust bearings in a vertical fluid displacement module
US8752674B2 (en) * 2010-12-17 2014-06-17 Vetco Gray Scandinavia As System and method for momentary hydrostatic operation of hydrodynamic thrust bearings in a vertical fluid displacement module
RU2458446C1 (ru) * 2011-01-24 2012-08-10 Владимир Петрович Глазков Электрическая машина
US20190154048A1 (en) * 2016-03-16 2019-05-23 Schaeffler Technologies AG & Co. KG Vehicle having a pump device
CN108779800A (zh) * 2016-03-18 2018-11-09 诺沃皮尼奥内技术股份有限公司 用于涡轮机械的磁性轴承
US20190048884A1 (en) * 2016-03-18 2019-02-14 Nuovo Pignone Tecnologie Srl Magnetic bearing for a turbomachine
US11002283B2 (en) * 2016-03-18 2021-05-11 Nuovo Pignone Tecnologie Srl Magnetic bearing for a turbomachine

Also Published As

Publication number Publication date
DE2336488A1 (de) 1975-02-06
GB1454205A (en) 1976-11-03
CS175480B2 (enrdf_load_stackoverflow) 1977-05-31
IT1015527B (it) 1977-05-20
PL91412B1 (enrdf_load_stackoverflow) 1977-02-28

Similar Documents

Publication Publication Date Title
US3947153A (en) Lubricated thrust bearings for pump and motor units
US5201642A (en) Magnetic drive pump
US3947154A (en) Pump assembly for circulation of coolant in boiling water reactors or the like
US3229130A (en) Motors having an air-gap jacket in particular for central heating accelerators and other like applications
US3002595A (en) Fluid coupling device
US6208512B1 (en) Contactless hermetic pump
US3430743A (en) Viscous oil flow hydraulic coupling
US3924715A (en) Clutch-brake unit
US3041976A (en) Motor pump construction
US3608910A (en) Shaft seal arrangements
US6254361B1 (en) Shaftless canned rotor inline pipe pump
US20090028731A1 (en) Ball bearing and a vacuum pump that is equipped with a bearing of this type
US2958292A (en) Canned motor
US4683111A (en) Gas circulator for a nuclear reactor and a method for use thereof
US4084924A (en) Pump-motor assemblage for circulating a coolant
US3030529A (en) Oil-cooled and -lubricated electric machine cooling system
US3035841A (en) Compensating seals
US20240380265A1 (en) Cooling system for load point dependent cooling of a rotor of an electric machine
EP1277965B1 (en) Centrifugal pump
US20140314599A1 (en) Centrifugal pump
US3134037A (en) Motor with hydrodynamic supported rotor
US3261295A (en) Motor driven pump
JPS626119B2 (enrdf_load_stackoverflow)
US3089045A (en) Coolant-circulating system for electric machines and the like
US4558870A (en) Mechanical seal assembly